bliss



Feb. 3, 1942. Ss 2,271,730

zzz/*E1 25.7,;

Feb. 3, 1942. s. c. Buss 2,271,730

PUMP

Filed July 1, i959 s sheets-sheet 2 l n a Feb. 3, 1942.

S. C. BLISS PUMP Filed July 1, 1939 S'Sheets-Sheet' 3 v Patented Feb. 3, 1942 UNITED STATES lPATENT OFFICE PUMP Sherwood C. Bliss, Buffalo, N. Y., assigner to Houde Engineering Corporation, Buffalo, N. Y., a corporation of New York Application July 1, 1939, Serial N0. 282,447

l Claim.

This invention relates to pumps and more particularly to pumps of the rotary type for delivering fluid, such as oil, under pressure to hydraulically operated devices.

An important object of the invention is to produce apump in which rotors of generally elliptical cross-section rotate in cylinders of circular crosssection, with the spaces between the rotors and cylinder Walls forming working chambers alternately connectable with fluid inlet and discharge i `for sealing the pump structure against the entrance of air, and to prevent the trapping or local accumulation of fluid particularly in the blade chambers so that the blades may at all times freely function for cooperation with the rotor elements.

Another important object is to provide improved sealing means for preventing the leakage of liuid from the pump structure. l

Still another object is to materially reduce the number of parts for the pump and to make a number of the parts interchangeable so as to facilitate assembly of the pump.

Ihe above enumerated and other important features of the invention are incorporated in the structure shown on the drawings, on which drawings:

Figure 1 is a plan view of the pump;

Figure 2 is an enlarged end view of the pump with the outer closure Wall and outer plate re moved and With the blade structure in section;

Figure 3 is a section onplane III-III, Figure 2;

Figure 4 is a section on plane IV-IV, Figure 3; and

Figures 5 and 5A diagrammatically show more clearly the cooperation of the rotors and blades for intake and discharge.

The pump housing comprises the cylindrical wall I having the inner head II integral therewith and having an outer closure and clamping head I2 insertable into the open end of the wall It. A drive shaft I3 extends through the passageway I4 of the head II and'has the reduced outer` end I which receives the inner ring of a ball bearing assembly I6 whose outer .ring is seated within the recess I'I provided in the outer wall I2. The reduced inner end I8 of the shaft receives the inner ring of a ball bearing assembly I5 whose outer ring is seated in the recess 20 provided in the head Il. A cover or retainer member 2I is secured to the outer end of the head I I asby screws 22 and has the passageway 23 for the end I8 of the shaft I3, the projecting end of the shaft being adapted to mount a driving source such as an electric motor (not shown). The member 2| may also serve as a bracket by means of which the pump structure may be supported.

The outer ring of the ball bearing assembly I3 is backed by a Washer 23 in the recess 20, and a recess v2li in the closure member 2I receives a washer 25, a steel washer 26 being interposed between the member 2I and the end of the head II and between the Washer 25 and the outer ring of the bearing assembly I9. Behind the washer 23 the head has a recess 2l for packing material 2l around the body of the shaft I3, and the Amember 2| has the recess 28 behind the Washer 25 for packing material 28 for surrounding the end It of the shaft, this packing material effecting a seal against escape of uid from the interior of the pump housing.

The pump cylinder forming elements are rings and plates clamped together between the inner face of the head I I and the clamping wall I2. As shown there are two rings 29 and 33 respectively, an inner plate 3l, an intermediate plate 32, and an outer plate 33, the outer diameters of the rings and plates being such that the rings and plates will lit snugly in the cylindrical bore of the wall I0. An annular clamping ring 3c has thread engagement in the outer end of the wall I0 and by the pressure exerted by this clamping ring, the pump rings and plates will be securely clamped between the inner face of the head II and the outer wall I2. To facilitate alignment of the rings and plates, they may lbe provided with holes 35 for dowel pins 36 which at their inner end may be anchored in the head I I, these dowel4 pins also preventing rotational displacement of the pump rings and plates.

The rings 29 and 30 and the plates 3l, 32, and 33 define annular cylinder spaces 31 and 35 into which the rotor members 39 and 4i) respectively extend to be rotated by the drive shaft I3, the shaft having splines or keyslll engaging in the keyways 42 in the rotors. As shown on Figure 3, the radial depth of the annular plates 3l, 32 and 33 is such that they will leave suicient clearance for operation of the shaft and the rotors.

Referring to Figure 2, the rotor elements 39 placed 90 on the shaft AI3 so that the opposite workingchambers 43 and 44 between the rotor 39 and the ring 29 will be displaced respectively 90 from the working chambers 45 and 45 between the rotor 49 and the ring 35.

The housing head I I is cored out to provide a f' suction or intake space S, and a discharge space D, the suction space or chamber Shaving the in let 4'1 connected by suitable piping with a source of uid such as oil, and the discharge space or chamber D having the outlet 48 connectable by suitable piping with hydraulic devices for receiving the fluid under pressure.

For the cylinder spaces3l and 38 Ain which thev rotors 39' and 49 operate; fluid inlet and outlet ports'are provided. As shown on Figure 2, each cylinder space has diametrically opposite inlet ports 49 and 49 and diametrically oppositel discharge'ports 5U and 59'.

Referring to Figure 3, the-rings 29` and 39 have transverse bores I therethrough for alignment with the transverse bores 52 in the plates 3l, 32 and 33 to form an intake' passageway which registers withthe inlet opening 53 in the head I I communicating with the intake or suction chamber S. The ports 49 extend'` radially from the bores 5I through the'rings 29 and 39to communicate with the cylinder spaces 31 land 38i so that the suction chamber S in the head is in communication with the cylinder spaces fora supply of uid thereto. Referring to Figure 2, the ring 29 has the cross wall or passageway 54 therethrough and the other ring 39 and the plates 3l, 32 and 33 have passageways therethrough registering with the passageway 54," to provide a discharge path connected with' the cylinder spaces 31 to 38 by way of the port 59,' and the passageway registering with the discharge opening 55 in the head II which communicates with the discharge chamber or space D inthe head. In like manner, the rings and plates are provided with registering cross bores to provide a passageway 56 between the ports 49' and' the opening 5l communicating with the inlet or suction chamber S in the head II. In the same manner a discharge passageway 58 is provided throughl the rings and walls for registering with the opening 59 communicating with the discharge chamber D inthe head VI I. The ports 49" connect the passageway 55 with the cylinder spaces 31 `and 38 and theports connect the discharge passageway 58 with the cylinder spaces as clearly shown on Figure 2.

Describing now the blade structure and operation, the rings 29 and 39 are each provided with diametrically opposite blades 68 (and GI for cooperating with the rotors surrounded by the respective rings. The blades operate in radially extending slots 52 cut into the rings from the inner surfaces thereof; each blade having a socket receiving the lower end of a stem 54which extends radially outwardly and is guided in a passageway 54 in the ring, the outer end of the pin' projecting into a plug 'seated in a threaded opening m. the cylindrical wall' I 9" of the pump housing. Each stem has a collar 6l between which and-.the head of the plug is interposed a compression' spring 63 so that the 'blade is yieldably shifted downwardly by the stem for engagement at its inner end with the surface of the respective rotor, the end of the blade being biased 01T as clearly shown on Figure 2 so as to have only edge engagement with the rotor. Referring to Figures 2 and 3, the upper blades BI are midway between the inlet and discharge passageways 56 and 58, while the lower blades 60 are midwaybetween the inlet anddischarge passageways 5I and 54, the blades being thus between the respective ports leading from the passageways to the cylinder faces of the rings. The rotor engaging edges of the blades are directed toward the respective discharge passageways, the rotors rotating inthe direction of the arrow on Figure 2.

Referring to the diagrammatic layout of Figure 5, the two rotors 39 and 40 are shown moving together'in direction of the arrows relative to the rings 29 and 30, 6I representing the upper blades located between the inlet and discharge passageways 56and 58 respectively from which the ports 494 and 59 leadv for cooperation with the working chambers 43, 44 and 45 and 46 under control of the blades. The bladey for theV rotor 39 is shown in engagement with the cylindrical portion of the rotor while the blade for the rotor 4U is in engagement with a cut away portion of the rotor which forms the Working chamber. Starting with the position shown in4 Figure 5, rotation of the rotors will carry the hydraulic chamber 48' past the blade SI which extends thereinto and the fluid will be forced 'out of this chamber into the port 59 and through passageway 58 into the discharge chamber D of the pump head II. While the chamber 46' at one side of'the blade is discharging, the portion of the chamber at the opposite side of the blade is increasing in size and therefore draws in fluid from the intake space S of the pump head and through the port 49.

While'the rotor 40 is thus discharging, a cylindrical portion of the rotor 39 is traveling pastv its blade 6I, the workingchamber 43, at the position shown in Figure 5, having just completed a fluid intake operation through the intake port 49. As vsoon'as the working chamber 44 of the rotor 39 reaches the blade 6I, this chamber will be discharged through the'outletl port 59', the discharge of this chamber being displaced from the discharge operation 'at'the chamber 46 in the rotor 40. At v 'of travel of the rotors, the working chamber 48 of the rotor 49 will receive the blade 60 (Figure 2) and the chamber will be discharged through the discharge port 59, and when the working chamber 44' reaches its blade 'it will be discharged 90 behind the discharge of the chamber'46 in rotor 4l). The` four working chambers of the two rotors being spaced 90 apart, each chamber will beilled and discharged twice for eachcomplete rotation of the rotors and balanced non-pulsating operation is assured with a constant rate .of discharge from the pump andfurthermore the hydraulic pressure on; the rotors'and the rotor shafts is balanced thus greatly reducing the load on the shaft bearings. Referring to Figure 2, it will be noted that there is sufficient clearance between the drive shaft I3 and the rotors'so that the rotors may at all times revolve freely in their'cylinder spaces without being subjected to any strain which might result from slight shaft bearing irregularity.

In order to effect sealing against escape of uid from the pump housing past the end wall I2, I

provide'this'wall with van' annular groove 69 atA its outer 'corner' forV 'a sealing 'ring '10" and 'which may be of rubber. A comparatively thin hard steel friction washer 'Il is applied against the outer side of the wall I2 and over the groove for engagement by the locking nut or ring 34. The pressure against the sealing ring will compress it for intimate engagement with the surrounding surfaces so as to effectively prevent leakage. The groove 69 is extended inwardly by a very narrow annular portion 12 around the t diameter of the wall l2. This extended portion constitutes a spill groove and it is made larger in area than the compression of the rubber of the sealing ring 1U will require so that any of the rubber in excess of that required to effect sealing may move into the spill groove.

As best shown on Figure 3, ports 13 are provided in the middle plate 32 for connecting the outer ends of adjacent blade slots 62 so that any uid leaking into the space at the backs of the blades can circulate back and forth between the two blades and act to accelerate the blades inwardly in cooperation with the blade accelerating springs 68. In order to prevent entrapping of oil behind the blades, which might interfere with their free and easy operation, release means are provided by connecting the valve slot spaces with either the discharge or the suction line. As shown on Figure 2, shallow channels 14 may be cut in the sides of the rings to connect the spaces behind the blades with the suction lines 5| and 56.

In order to prevent accumulation and entrapping of uid in the space between the drive shaft and the pump operating parts, release channels 15 may be provided, these channels, as shown, being cut in the outer faces of the platesv3l `and 33 for flow of surplus fluid from the space around the shaft to the suction line. Shallow channels 16 may also be cut in the inner face of the rings so that any fluid which may be trapped between the blades and the rotors may flow into the discharge outlet.

It will be noted that in the pump shown and described, the rotors are alike, and likewise the rings and the separator plates are alike, so that these parts may be interchangeably used thus making for quick and easy assembly. These various parts may be inexpensively made as no costly precision work is required.

I have shown a practical and eflicient embodiment of the various features of my invention but I do not desire to be limited to lthe exact construction, arrangement and operation shown and described as changes and modications may be made without departing from the scope of the invention.

I claim as my invention:

A cylinder structure for fluid under pressure comprising a cylindrical wall having a removable end wall fitting into one end thereof to form a closure therefor, a clamping ring having threaded engagement with said cylindrical Wall outside of said end wall for clamping said end wall in place, a thin metallic washer between said clamping ring n and said end wall, the outer peripheral corner 

